EP0443472B1 - Confining liquid-sealing arrangement for a turbo compressor - Google Patents

Confining liquid-sealing arrangement for a turbo compressor Download PDF

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Publication number
EP0443472B1
EP0443472B1 EP91102226A EP91102226A EP0443472B1 EP 0443472 B1 EP0443472 B1 EP 0443472B1 EP 91102226 A EP91102226 A EP 91102226A EP 91102226 A EP91102226 A EP 91102226A EP 0443472 B1 EP0443472 B1 EP 0443472B1
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EP
European Patent Office
Prior art keywords
sealing liquid
pressure
sealing
gas
seal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP91102226A
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German (de)
French (fr)
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EP0443472A1 (en
Inventor
Helmut Schellong
Karl-Heinz Victor
Hans-Wilhelm Laarmann
Gustav Maser
Ralf Dr. Dedeken
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Pacific Wietz GmbH and Co KG
Vodafone GmbH
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Pacific Wietz GmbH and Co KG
Mannesmann AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/918—Seal combined with filter or fluid separator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/927—Seal including fluid pressure differential feature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/93—Seal including heating or cooling feature

Definitions

  • the invention relates to a sealing fluid sealing arrangement for the shaft sealing in a turbocompressor, in particular in a high-pressure turbocompressor, with the features of the preamble of patent claim 1.
  • the barrier liquid sealing arrangement known from practice, from which the invention is based, works with floating ring seals.
  • Floating ring seals are radial gap seals with play between the rotating shaft and the sealing rings that are connected to the seal housing but can move radially.
  • the pressure of the sealing liquid is greater than the gas pressure to be sealed.
  • the pressure difference is small in the context of the known measures, for example it is 0.5 bar. It is small in order to keep the amount of internal leakage on the gas-side sealing ring small.
  • the radial gap on the outer sealing ring is dimensioned such that the barrier liquid flow necessary for cooling the gas-side sealing ring is established as a coolant flow. This coolant flow is approximately proportional to the sealing pressure.
  • the amount of sealing fluid stored in the elevated tank must be so large that controlled shutdown of the turbocompressor system is possible if the sealing fluid supply fails. If the system stops under pressure, the sealing liquid system must be kept in operation.
  • the barrier fluid system is an open system. For the rest, the measures described are complex. A similar arrangement is known from GB-A-1 360 117.
  • the object of the invention is to create a sealing liquid sealing arrangement which is constructed much more simply, works with low internal leakage quantities and also permits differential pressure control in a simple manner.
  • the gas-side seal preferably works in the mixed friction area.
  • Various arrangements of the slide rings can be used within the scope of the invention.
  • An embodiment in which the gas-side slide ring is held axially and radially by a bellows surrounding the shaft and the atmosphere-side slide ring by secondary elements, for example in the form of springs and at least one O-ring, are distinguished by simplicity and functional reliability.
  • the contact forces of the gas-side slide ring are determined by the bellows and the effective hydraulic differential pressure between sealing liquid and gas.
  • the contact forces of the slide ring on the atmosphere side are determined by the springs and the effective hydraulic pressure of the sealing liquid.
  • the bellows can be replaced by other sealing systems, in particular by an O-ring and spring elements.
  • the internal leakage quantities of the sealing liquid are generally conducted to separators via a line.
  • the gas-side seal is a mechanical seal with low leakage values, which preferably works in the mixed friction area.
  • the atmosphere-side seal is an axial gap seal, the sealing surfaces of which are separated in the dynamic state by a hydrodynamically designed liquid film.
  • Mixed friction occurs when there is a load-bearing lubricating film in the sealing gap, but this is interrupted in places.
  • the sliding properties of the pair of sliding materials also begin to influence the friction behavior or the coefficient of friction.
  • the coefficient of friction is determined solely by the dynamic viscosity of the lubricant. The amount of leakage flowing out can be used to check the function of the overall system.
  • the barrier liquid circuit is closed. This means that the sealing liquid remains at the sealing pressure level in the sealing liquid sealing arrangement according to the invention. It is pumped around by a circuit pump, which has to overcome the flow resistances of the closed circuit. The heat loss of the seals is dissipated to the cooler.
  • the very small, adjustable leakage quantity emerging from the closed sealing liquid circuit via the axial gaps of the slide rings is intermittently replaced by a small feed pump.
  • the advantages achieved are mainly to be seen in the fact that the amount of leakage in the sealing liquid sealing arrangement according to the invention is very much smaller than in the embodiment with floating ring seals described at the beginning. Operation with a closed barrier liquid circuit is therefore possible without difficulty and the differential pressure control can also be carried out in a simple manner.
  • the system as a whole is simple because elevated tanks and barrier fluid pumps of high performance and the usual differential pressure control valves are no longer required. The result is considerable energy savings.
  • the cooling of the seal is independent of the pressure level.
  • the small amount of internal leakage and the tightness against standstill are also of particular advantage.
  • the slide rings and the rotor ring can be easily constructed from materials with a long service life. In general, hard / hard pairing is used and the slide rings and the rotor ring are practically wear-free.
  • the sealing liquid sealing arrangement shown in the figures initially includes a gas-side axially sealing slide ring 1 and an atmosphere-side axially sealing slide ring 2, both of which are fixedly arranged in the seal housing 3. It also includes a rotor ring 5 connected to the shaft 4 with opposing sealing surfaces, to which the sliding rings 1, 2 are assigned with their sealing surfaces.
  • a sealing liquid space 6 or 7 is assigned to both sliding rings 1, 2.
  • the two barrier liquid spaces 6, 7 are connected to one another on the circumferential side of the rotor ring 5 via the ring channel 8.
  • the atmosphere-side slide ring 2 seals the assigned barrier liquid space 6 against the atmosphere.
  • the gas-side slide ring 1 seals the assigned barrier liquid space 7 against the gas space.
  • the two sealing liquid spaces 6, 7 belong to a closed sealing liquid circuit 9 with pump 10 and cooler 11.
  • the pump provided with the reference number 10 in the diagram could also work with the rotor ring 5 as a pump rotor and would then be integrated into the sealing arrangement.
  • Fig. 2 it can be seen that the gas-side slide ring 1 is held by a bellows 12 surrounding the shaft 4.
  • the atmosphere-side slide ring 2 is held axially and radially by secondary elements in the form of springs 13 and O-rings 14.
  • the internal leakage amounts of the Barrier liquid are led to a separator 24 via a line 23. After any preparation, this amount of leakage is fed to the tank 16.
  • the external leaks of the sealing liquid are led to the tank 16 via a line 15.
  • the quantity of sealing liquid in the sealing liquid circuit is replenished via a feed pump 17 and a pressure booster 18.
  • the pressure intensifier 18 is acted on the one hand by the gas to be sealed and by an adjustable spring (not shown), and on the other hand by the sealing liquid in the sealing liquid circuit.
  • the pressure in the sealing liquid circuit and thus the pressure difference between sealing liquid and gas to be sealed can be determined by adjusting the spring.
  • the pressure booster 18 is also designed as a barrier fluid reservoir.
  • the pressure difference between the gas to be sealed and the sealing liquid is generated in the pressure booster 18.
  • the pressure intensifier 18 consists in detail of a pressure cylinder 19 in which a piston 20 is arranged to be axially movable. One side of the piston 20 is acted on by the sealing liquid and the other side is acted on by the gas to be sealed. On the gas side, a spring force acts in addition to the gas pressure. This creates a pressure difference between sealing liquid and gas.
  • the differential pressure is kept in a predetermined range and is independent of the pressure level. Since the pressure intensifier 18 is also a barrier fluid reservoir, a controlled shutdown of the turbocompressor and a longer standstill under pressure are possible even if the power supply to the feed pumps fails.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Compressor (AREA)

Description

Die Erfindung betrifft eine Sperrflüssigkeits-Dichtungsanordnung für die Wellenabdichtung bei einem Turboverdichter, insbesondere bei einem Hochdruck-Turboverdichter, mit den Merkmalen des Oberbegriffs des Patentanspruchs 1.The invention relates to a sealing fluid sealing arrangement for the shaft sealing in a turbocompressor, in particular in a high-pressure turbocompressor, with the features of the preamble of patent claim 1.

Die aus der Praxis bekannte Sperrflüssigkeits-Dichtungsanordnung, von der die Erfindung ausgeht, arbeitet mit Schwimmringdichtungen. Schwimmringdichtungen sind Radialspaltdichtungen mit Spiel zwischen der rotierenden Welle und den mit dem Dichtungsgehäuse verbundenen, aber radialbeweglichen Dichtringen. Dem Zwecke einer Sperrflüssikgeits-Dichtungsanordnung entsprechend ist der Druck des Sperrflüssigkeit größer als der abzudichtende Gasdruck. Die Druckdifferenz ist im Rahmen der bekannten Maßnahmen klein, sie liegt beispielsweise bei 0,5 bar. Sie ist klein, um die Innenleckagemenge an dem gasseitigen Dichtungsring klein zu halten. Der Radialspalt an dem äußeren Dichtungsring ist so bemessen, daß sich der zur Kühlung des gasseitigen Dichtungsringes nötige Sperrflüssigkeitsstrom als Kühlmittelstrom einstellt. Dieser Kühlmittelstrom ist etwa proportional dem Abdichtdruck. Das bedeutet, daß eine optimal Kühlung nur für einen bestimmten Druckbereich gegeben ist und daß sich für Turboverdichter, die in einem großen Druckbereich arbeiten, Einschränkungen ergeben können. Hinzu kommt, daß bei höheren Drücken die Regelung des Differenzdruckes zwischen der Sperrflüssigkeit einerseits und dem abzudichtenden Gas andererseits schwierig ist, weil der Differenzdruck im Vergleich zu dem abzudichtenden Gasdruck sehr klein wird. Die Regelung erfolgt durch eine Vordrucksteuerung und eine indirekte Differenzdruckregelung durch Regelung des Flüssigkeitsniveaus für die Sperrflüssigkeit in einem Hochbehälter. Der erzeugte Differenzdruck ist proportional der geodätischen Höhe der Sperrflüssigkeitsmenge im Hochbehälter relativ zur Welle des Turboverdichters. Die Sperrflüssigkeit wird durch Hochdruckpumpen auf Druck gebracht und im Radialspalt der äußeren Schwimmringe auf Atmosphärendruck entspannt. Die im Hochbehälter gespeicherte Sperrflüssigkeitsmenge muß so groß sein, daß bei Ausfall der Sperrflüssigkeitsversorgung ein geregeltes Abfahren der Turboverdichteranlage möglich ist. Bei Stillstand der Anlage unter Druck muß die Sperrflüssigkeitsanlage in Betrieb gehalten werden. Das Sperrflüssigkeitssystem ist insoweit ein offenes System. Im übrigen sind die beschriebenen Maßnahmen aufwendig. Eine ähnliche Anordnung ist aus der GB-A-1 360 117 bekannt.The barrier liquid sealing arrangement known from practice, from which the invention is based, works with floating ring seals. Floating ring seals are radial gap seals with play between the rotating shaft and the sealing rings that are connected to the seal housing but can move radially. Corresponding to the purpose of a sealing liquid sealing arrangement, the pressure of the sealing liquid is greater than the gas pressure to be sealed. The pressure difference is small in the context of the known measures, for example it is 0.5 bar. It is small in order to keep the amount of internal leakage on the gas-side sealing ring small. The radial gap on the outer sealing ring is dimensioned such that the barrier liquid flow necessary for cooling the gas-side sealing ring is established as a coolant flow. This coolant flow is approximately proportional to the sealing pressure. This means that optimal cooling is only provided for a certain pressure range and that restrictions can arise for turbocompressors which operate in a large pressure range. In addition, at higher pressures it is difficult to regulate the differential pressure between the barrier liquid on the one hand and the gas to be sealed on the other hand, because the differential pressure becomes very small compared to the gas pressure to be sealed. The regulation is carried out by a form pressure control and an indirect differential pressure regulation by regulating the liquid level for the barrier liquid in an elevated tank. The differential pressure generated is proportional to the geodetic amount of the barrier fluid in the elevated tank relative to the shaft of the turbocompressor. The sealing liquid is brought to pressure by high pressure pumps and expanded to atmospheric pressure in the radial gap of the outer floating rings. The amount of sealing fluid stored in the elevated tank must be so large that controlled shutdown of the turbocompressor system is possible if the sealing fluid supply fails. If the system stops under pressure, the sealing liquid system must be kept in operation. The barrier fluid system is an open system. For the rest, the measures described are complex. A similar arrangement is known from GB-A-1 360 117.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Sperrflüssigkeits-Dichtungsanordnung zu schaffen, die sehr viel einfacher aufgebaut ist, mit geringen Innenleckagemengen arbeitet und auf einfache Weise auch die Differenzdruckregelung zuläßt.In contrast, the object of the invention is to create a sealing liquid sealing arrangement which is constructed much more simply, works with low internal leakage quantities and also permits differential pressure control in a simple manner.

Diese Aufgabe wird gelöst mit der Sperrflüssigkeits-Dichtungsanordnung nach Patentanspruch 1. Die gasseitige Dichtung arbeitet vorzugsweise im Mischreibungsbereich. Im Rahmen der Erfindung kann mit verschiedenen Anordnungen der Gleitringe gearbeitet werden. Durch Einfachheit und Funktionssicherheit ausgezeichnet ist ein Ausführungsform, bei der der gasseitige Gleitring von einem die Welle umgebenden Faltenbalg sowie der atmosphärenseitige Gleitring durch Sekundärelemente, z.B. in Form von Federn und zumindest einem O-Ring, axial- und radialbeweglich gehalten ist. Die Anpreßkräfte des gasseitigen Gleitringes werden bestimmt durch den Faltenbalg und den wirksamen hydraulischen Differenzdruck zwischen Sperrflüssigkeit und Gas. Die Anpreßkräfte des atmosphärenseitigen Gleitringes werden bestimmt durch die Federn und den wirksamen hydraulischen Druck der Sperrflüssigkeit. Es versteht sich, daß der Faltenbalg durch andere Dichtsysteme, insbesondere durch einen O-Ring und Federelemente, ersetzt werden kann. Im Rahmen der Erfindung sind die Innenleckagemengen der Sperrflüssigkeit im allgemeinen über eine Leitung zu Abscheidern geführt.This object is achieved with the sealing liquid sealing arrangement according to claim 1. The gas-side seal preferably works in the mixed friction area. Various arrangements of the slide rings can be used within the scope of the invention. An embodiment in which the gas-side slide ring is held axially and radially by a bellows surrounding the shaft and the atmosphere-side slide ring by secondary elements, for example in the form of springs and at least one O-ring, are distinguished by simplicity and functional reliability. The contact forces of the gas-side slide ring are determined by the bellows and the effective hydraulic differential pressure between sealing liquid and gas. The contact forces of the slide ring on the atmosphere side are determined by the springs and the effective hydraulic pressure of the sealing liquid. It goes without saying that the bellows can be replaced by other sealing systems, in particular by an O-ring and spring elements. In the context of the invention, the internal leakage quantities of the sealing liquid are generally conducted to separators via a line.

Bei der erfindungsgemäßen Sperrflüssigkeits-Dichtungsanordnung ist die gasseitige Dichtung eine Gleitringdichtung mit niedrigen Leckagewerten, die vorzugsweise im Mischreibungsgebiet arbeitet. Die atmosphärenseitige Dichtung ist eine Axialspaltdichtung, deren Dichtflächen im dynamischen Zustand durch einen hydrodynamisch ausgebildeten Flüssigkeitsfilm getrennt sind. Mischreibung liegt vor, wenn sich im Dichtspalt zwar ein tragender Schmierfilm befindet, dieser jedoch stellenweise unterbrochen ist. Neben den Eigenschaften des Schmierstoffes beginnen auch die Gleiteigenschaften der Gleitwerkstoffpaarung das Reibverhalten bzw. die Reibungszahl zu beeinflussen. Bei der Flüssigkeitsreibung mit einem hydrodynamisch ausgebildeten Flüssigkeitsfilm wird die Reibzahl allein durch die dynamische Zähigkeit des Schmierstoffes bestimmt. Die nach außen abfließende Leckagemenge kann zur Funktionskontrolle des Gesamtsystems herangezogen werden. Sie ist stets so klein einrichtbar, daß die weiteren im System befindlichen Regeleinrichtungen niemals ihre betriebssichernden Regelbereiche überschreiten. Der Sperrflüssigkeitskreis ist geschlossen. Das bedeutet, daß die Sperrflüssigkeit bei der erfindungsgemäßen Sperrflüssigkeits-Dichtungsanordnung auf dem Abdichtdruckniveau bleibt. Sie wird durch eine Kreislaufpumpe, welche die Strömungswiderstände des geschlossenen Kreislaufs überwinden muß, umgepumpt. Die Verlustleistung der Dichtungen wird an den Kühler abgeführt. Die aus dem geschlossenen Sperrflüssigkeitskreis über die Axialspalte der Gleitringe austretende sehr kleine einstellbare Leckmenge wird intermittierend über eine kleine Speisepumpe ersetzt.In the sealing liquid sealing arrangement according to the invention, the gas-side seal is a mechanical seal with low leakage values, which preferably works in the mixed friction area. The atmosphere-side seal is an axial gap seal, the sealing surfaces of which are separated in the dynamic state by a hydrodynamically designed liquid film. Mixed friction occurs when there is a load-bearing lubricating film in the sealing gap, but this is interrupted in places. In addition to the properties of the lubricant, the sliding properties of the pair of sliding materials also begin to influence the friction behavior or the coefficient of friction. When fluid friction with a hydrodynamic trained liquid film, the coefficient of friction is determined solely by the dynamic viscosity of the lubricant. The amount of leakage flowing out can be used to check the function of the overall system. It can always be set up so small that the other control devices in the system never exceed their operationally secure control ranges. The barrier liquid circuit is closed. This means that the sealing liquid remains at the sealing pressure level in the sealing liquid sealing arrangement according to the invention. It is pumped around by a circuit pump, which has to overcome the flow resistances of the closed circuit. The heat loss of the seals is dissipated to the cooler. The very small, adjustable leakage quantity emerging from the closed sealing liquid circuit via the axial gaps of the slide rings is intermittently replaced by a small feed pump.

Die erreichten Vorteile sind hauptsächlich darin zu sehen, daß bei der erfindungsgemäßen Sperrflüssigkeits-Dichtungsanordnung die Leckagemenge sehr viel kleiner ist als bei der eingangs beschriebenen Ausführungsform mit Schwimmringdichtungen. Daher ist ohne Schwierigkeiten der Betrieb mit einem geschlossenen Sperrflüssigkeitskreis möglich und kann auf einfache Weise auch die Differenzdruckregelung durchgeführt werden. Das System insgesamt ist einfach, weil Hochbehälter und Sperrflüssigkeitspumpen hoher Leistung sowie die dazu üblichen Differenzdruckregelventile nicht mehr erforderlich sind. Im Ergebnis erreicht man eine beachtliche Energieersparnis. Die Kühlung der Dichtung ist unabhängig vom Druckniveau. Von besonderem Vorteil sind fernerhin die kleinen Innenleckagemenge und die Stillstandsdichtheit. Die Gleitringe und der Rotorring lassen sich ohne weiteres aus Werkstoffen hoher Standzeit aufbauen. Im allgemeinen wird mit Hart/Hart-Paarung gearbeitet und sind die Gleitringe sowie der Rotorring praktisch verschleißfrei.The advantages achieved are mainly to be seen in the fact that the amount of leakage in the sealing liquid sealing arrangement according to the invention is very much smaller than in the embodiment with floating ring seals described at the beginning. Operation with a closed barrier liquid circuit is therefore possible without difficulty and the differential pressure control can also be carried out in a simple manner. The system as a whole is simple because elevated tanks and barrier fluid pumps of high performance and the usual differential pressure control valves are no longer required. The result is considerable energy savings. The cooling of the seal is independent of the pressure level. The small amount of internal leakage and the tightness against standstill are also of particular advantage. The slide rings and the rotor ring can be easily constructed from materials with a long service life. In general, hard / hard pairing is used and the slide rings and the rotor ring are practically wear-free.

Im folgenden wird die Erfindung anhand einer lediglich ein Ausführungsbeispiel darstellenden Zeichnung ausführlicher erläutert. Es zeigen

Fig. 1
eine schematische Darstellung eines Turboverdichters mit erfindungsgemäßer Sperrflüssigkeits-Dichtungsanordnung und
Fig. 2
in gegenüber der Fig. 1 wesentlich vergrößertem Maßstab einen Axialschnitt durch die linke der Sperrflüssigkeits-Dichtungsanordnungen des Turboverdichters in Fig. 1.
In the following, the invention will be explained in more detail with reference to a drawing showing only one exemplary embodiment. Show it
Fig. 1
a schematic representation of a turbocompressor with the inventive sealing liquid sealing arrangement and
Fig. 2
In an enlarged scale compared to FIG. 1, an axial section through the left of the sealing fluid sealing arrangements of the turbocompressor in FIG. 1.

Zu der Sperrflüssigkeits-Dichtungsanordnung, die in den Figuren dargestellt ist, gehören zunächst ein gasseitiger axial dichtender Gleitring 1 und ein atmosphärenseitiger axial dichtender Gleitring 2, die beide fest im Dichtungsgehäuse 3 angeordnet sind. Es gehört dazu fernerhin ein mit der Welle 4 verbundener Rotorring 5 mit einander gegenüberliegenden Dichtflächen, denen die Gleitringe 1, 2 mit ihren Dichtflächen zugeordnet sind. Beiden Gleitringen 1, 2 ist ein Sperrflüssigkeitsraum 6 bzw. 7 zugeordnet. Die beiden Sperrflüssigkeitsräume 6, 7 stehen an der Umfangsseite des Rotorringes 5 über den Ringkanal 8 miteinander in Verbindung. Der atmosphärenseitige Gleitring 2 dichtet den zugeordneten Sperrflüssigkeitsraum 6 gegen die Atmosphäre ab. Der gasseitige Gleitring 1 dichtet den zugeordneten Sperrflüssigkeitsraum 7 gegen den Gasraum ab. Die beiden Sperrflüssigkeitsräume 6, 7 gehören einem geschlossenen Sperrflüssigkeitskreis 9 mit Pumpe 10 und Kühler 11 an. Die im Schema mit dem Bezugszeichen 10 versehene Pumpe könnte auch mit dem Rotorring 5 als Pumpenrotor arbeiten und wäre dann in die Dichtungsanordnung integriert. Aus der Fig. 2 entnimmt man, daß der gasseitige Gleitring 1 von einem die Welle 4 umgebenden Faltenbalg 12 gehalten ist. Der atmosphärenseitige Gleitring 2 ist durch Sekundärelemente in Form von Federn 13 und O-Ringen 14 axial- und radialbeweglich gehalten. Die Innenleckagemengen der Sperrflüssigkeit sind über eine Leitung 23 zu einem Abscheider 24 geführt. Nach eventueller Aufbereitung wird diese Leckmenge dem Tank 16 zugeführt. Die Außenleckagen der Sperrflüssigkeit sind über eine Leitung 15 zu dem Tank 16 geführt. Die Sperrflüssigkeitsmenge im Sperrflüssigkeitskreis wird über eine Speisepumpe 17 und einen Druckübersetzer 18 wieder aufgefüllt. Der Druckübersetzer 18 ist einerseits von dem abzudichtenden Gas und von einer nicht gezeichneten einstellbaren Feder beaufschlagt, andererseits von der Sperrflüssigkeit im Sperrflüssigkeitskreis. Über die Einstellung der Feder können der Druck im Sperrflüssigkeitskreis und damit die Druckdifferenz zwischen Sperrflüssigkeit und abzudichtendem Gas bestimmt werden. Der Druckübersetzer 18 ist gleichzeitig als Sperrflüssigkeitsspeicher ausgebildet.The sealing liquid sealing arrangement shown in the figures initially includes a gas-side axially sealing slide ring 1 and an atmosphere-side axially sealing slide ring 2, both of which are fixedly arranged in the seal housing 3. It also includes a rotor ring 5 connected to the shaft 4 with opposing sealing surfaces, to which the sliding rings 1, 2 are assigned with their sealing surfaces. A sealing liquid space 6 or 7 is assigned to both sliding rings 1, 2. The two barrier liquid spaces 6, 7 are connected to one another on the circumferential side of the rotor ring 5 via the ring channel 8. The atmosphere-side slide ring 2 seals the assigned barrier liquid space 6 against the atmosphere. The gas-side slide ring 1 seals the assigned barrier liquid space 7 against the gas space. The two sealing liquid spaces 6, 7 belong to a closed sealing liquid circuit 9 with pump 10 and cooler 11. The pump provided with the reference number 10 in the diagram could also work with the rotor ring 5 as a pump rotor and would then be integrated into the sealing arrangement. From Fig. 2 it can be seen that the gas-side slide ring 1 is held by a bellows 12 surrounding the shaft 4. The atmosphere-side slide ring 2 is held axially and radially by secondary elements in the form of springs 13 and O-rings 14. The internal leakage amounts of the Barrier liquid are led to a separator 24 via a line 23. After any preparation, this amount of leakage is fed to the tank 16. The external leaks of the sealing liquid are led to the tank 16 via a line 15. The quantity of sealing liquid in the sealing liquid circuit is replenished via a feed pump 17 and a pressure booster 18. The pressure intensifier 18 is acted on the one hand by the gas to be sealed and by an adjustable spring (not shown), and on the other hand by the sealing liquid in the sealing liquid circuit. The pressure in the sealing liquid circuit and thus the pressure difference between sealing liquid and gas to be sealed can be determined by adjusting the spring. The pressure booster 18 is also designed as a barrier fluid reservoir.

Die Druckdifferenz zwischen dem abzudichtenden Gas und der Sperrflüssigkeit wird in dem Druckübersetzer 18 erzeugt. Der Druckübersetzer 18 besteht im einzelnen aus einem Druckzylinder 19, in dem ein Kolben 20 axialbeweglich angeordnet ist. Die eine Seite des Kolbens 20 wird mit der Sperrflüssigkeit und die andere Seite wird mit dem abzudichtenden Gas beaufschlagt. Auf der Gasseite greift zusätzlich zum Gasdruck noch eine Federkraft an. Diese erzeugt eine Druckdifferenz zwischen Sperrflüssigkeit und Gas. Der Differenzdruck wird in einem vorgegebenen Bereich gehalten und ist unabhängig vom Druckniveau. Da der Druckübersetzer 18 gleichzeitig Sperrflüssigkeitsspeicher ist, sind auch bei Ausfall der Energieversorgung der Speisepumpen ein geregeltes Abfahren des Turboverdichters und ein längerer Stillstand unter Druck möglich.The pressure difference between the gas to be sealed and the sealing liquid is generated in the pressure booster 18. The pressure intensifier 18 consists in detail of a pressure cylinder 19 in which a piston 20 is arranged to be axially movable. One side of the piston 20 is acted on by the sealing liquid and the other side is acted on by the gas to be sealed. On the gas side, a spring force acts in addition to the gas pressure. This creates a pressure difference between sealing liquid and gas. The differential pressure is kept in a predetermined range and is independent of the pressure level. Since the pressure intensifier 18 is also a barrier fluid reservoir, a controlled shutdown of the turbocompressor and a longer standstill under pressure are possible even if the power supply to the feed pumps fails.

Claims (3)

  1. A sealing liquid seal arrangement for the shaft seal in a turbocompressor, particularly in a high-pressure turbocompressor, with a sliding ring (1) providing an axial seal on the gas side and a sliding ring (2) providing an axial seal on the atmosphere side, which are both disposed fixed in the housing (3), and a rotor ring (5) attached to the shaft (4) and having opposite seal faces with which the seal faces of the sliding rings (1, 2) are associated, wherein a sealing liquid space (6; 7) is associated with both sliding rings (1, 2), which sealing liquid spaces (6, 7) are connected to each other at the peripheral face of the rotor ring (5) via an annular channel (8), wherein the sliding ring (2) on the atmosphere side seals the associated sealing liquid space (6) from the atmosphere and the sliding ring (1) on the gas side seals the associated sealing liquid space (7) from the gas space, characterised in that the two sealing liquid spaces (6, 7) form part of a closed sealing liquid circuit (9) with a pump (10) and a cooling device (11) and the amount of sealing liquid in the sealing liquid circuit (9) can be topped up again via a supply pump (17) and a pressure intensifier (18), wherein the pressure intensifier (18) is acted upon on one side by the gas to be sealed and by an adjustable spring force and is acted upon on the other side by the sealing liquid in the sealing liquid circuit, that the pressure intensifier (18) sets a pressure difference between the sealing liquid and the gas irrespective of the pressure level and determines the pressure in the sealing liquid circuit (9), and that the pressure intensifier (18) is at the same time constructed as a sealing liquid store.
  2. A sealing liquid seal arrangement according to claim 1, wherein the sliding ring (1) on the gas side is held by an expanding bellows (12) surrounding the shaft (4) and the sliding ring (2) on the atmosphere side is held by secondary elements (13, 14) so that it is axially and radially movable.
  3. A sealing liquid seal arrangement according to either one of claims 1 or 2, characterised in that the amounts of internal leakage of the sealing liquid are conveyed to separators (24) via a line (23).
EP91102226A 1990-02-21 1991-02-16 Confining liquid-sealing arrangement for a turbo compressor Expired - Lifetime EP0443472B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4005427A DE4005427C1 (en) 1990-02-21 1990-02-21
DE4005427 1990-02-21

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EP0443472A1 EP0443472A1 (en) 1991-08-28
EP0443472B1 true EP0443472B1 (en) 1994-08-24

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EP91102226A Expired - Lifetime EP0443472B1 (en) 1990-02-21 1991-02-16 Confining liquid-sealing arrangement for a turbo compressor

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US (1) US5158431A (en)
EP (1) EP0443472B1 (en)
DE (2) DE4005427C1 (en)
NO (1) NO172510C (en)

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CN109790929B (en) 2016-06-10 2021-05-07 约翰起重机英国有限公司 Dry gas seal with electronically controlled shut-off valve
EP3625486B1 (en) 2017-05-15 2022-10-19 John Crane UK Ltd. Dry gas seal with electronically controlled carrier load
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CN120061343B (en) * 2025-04-28 2025-07-01 山西省水利建筑工程局集团有限公司 A kind of bored pile desilting device and desilting method

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Also Published As

Publication number Publication date
NO910655L (en) 1991-08-22
DE59102588D1 (en) 1994-09-29
US5158431A (en) 1992-10-27
NO172510B (en) 1993-04-19
DE4005427C1 (en) 1991-07-25
NO910655D0 (en) 1991-02-19
NO172510C (en) 1993-07-28
EP0443472A1 (en) 1991-08-28

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